US8572962B2 - Exhaust gas recirculation system - Google Patents

Exhaust gas recirculation system Download PDF

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Publication number
US8572962B2
US8572962B2 US12/891,396 US89139610A US8572962B2 US 8572962 B2 US8572962 B2 US 8572962B2 US 89139610 A US89139610 A US 89139610A US 8572962 B2 US8572962 B2 US 8572962B2
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United States
Prior art keywords
exhaust gas
heat exchanger
gas recirculation
point
recirculation system
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Expired - Fee Related, expires
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US12/891,396
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English (en)
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US20110072808A1 (en
Inventor
Hans-Ulrich Steurer
Eberhard Pantow
Jérôme Genoist
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Mahle Behr France Rouffach SAS
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Behr GmbH and Co KG
Behr France Rouffach SAS
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Assigned to BEHR GMBH & CO. KG, BEHR FRANCE ROUFFACH SAS reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENOIST, JEROME, PANTOW, EBERHARD, STEURER, HANS-ULRICH
Publication of US20110072808A1 publication Critical patent/US20110072808A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/07—Mixed pressure loops, i.e. wherein recirculated exhaust gas is either taken out upstream of the turbine and reintroduced upstream of the compressor, or is taken out downstream of the turbine and reintroduced downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/33—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage controlling the temperature of the recirculated gases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to an exhaust gas recirculation system having an internal combustion engine, which is supplied with exhaust gas, diverted at a removal point and returned via a return point, and/or charge air, having a heat exchanger, arranged between the removal point and the return point, for the returned exhaust gas and/or the charge air, and having an exhaust gas recirculation valve, by means of which the amount of returned exhaust gas and/or charge air can be regulated.
  • An exhaust gas recirculation line with a heat exchanger is known from the DE 698 17 294 T2 of the European Pat. App. No. EP 0 913 561 B1, which corresponds to U.S. Pat. No. 6,155,042, which is arranged between an engine and a catalyst container in series with restriction component for generating back pressure, whereby the heat exchanger flow is upstream of the restriction component.
  • an exhaust gas recirculation valve is connected downstream of the heat exchanger.
  • a throttle plate is connected parallel to the heat exchanger.
  • An exhaust gas line for an internal combustion engine with a circulation line is known from the German patent publication No. DE 103 92 766 T5, which is connected directly or indirectly to an exhaust gas channel, for recycling a fraction of the exhaust gases.
  • a heat exchanger is connected between an exhaust gas catalyst container and a catalytic element.
  • An exhaust gas system for a heat engine with a waste heat recovery region for recovering heat from the exhaust gas and transferring the recovered heat to a heating medium, which is arranged in the exhaust gas line, is known from the unexamined German Pat. App. No. DE 102 59 702 A1.
  • a burner which is also called a combustor, is provided in the exhaust gas line.
  • an exhaust gas recirculation system having an internal combustion engine, which is supplied with exhaust gas, diverted at a removal point and returned via a return point, and/or charge air, having a heat exchanger, arranged between the removal point and the return point, for the returned exhaust gas and/or the charge air, and having an exhaust gas recirculation valve, by means of which the amount of returned exhaust gas and/or charge air can be regulated, is achieved in that the exhaust gas recirculation valve is connected between the removal point and the heat exchanger. All of the exhaust gas diverted at the removal point or all of the charge air diverted there is taken via the exhaust gas recirculation valve for heat exchange by the heat exchanger.
  • An exemplary embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger is assigned a diverter valve through which the exhaust gas, diverted at the removal point and emerging from the heat exchanger, and/or the charge air are returned via the return point or removed via a branch line.
  • the exhaust gas and/or the charge air diverted at the removal point, at least partially, together with the exhaust gas not diverted at the removal point can be discharged into the environment via the diverter valve by means of an exhaust system, which optionally comprises a catalytic device.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas, diverted at the removal point and emerging from heat exchanger, and/or charge air are returned by the diverter valve totally or partially via the return point or discharged via the branch line.
  • the heat exchanger can be used in one regard in a warm-up phase of the internal combustion engine to cool the exhaust gas diverted at the removal point for heat recovery. Moreover, the heat exchanger can be used to cool the exhaust gas returned to the return point to recover heat.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the diverter valve is integrated into the heat exchanger.
  • the exhaust gas recirculation valve can be integrated into the heat exchanger.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the diverter valve is provided at the outlet of the heat exchanger. It is achieved thereby in a simple manner that all of the exhaust gas diverted at the removal point is first subjected to a heat exchange.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas diverted at the removal point and/or the charge air can flow or do flow through the heat exchanger only in one direction.
  • a heat exchanger of this type is also called an I-flow heat exchanger.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the branch line and a return line are connected to one end of the heat exchanger.
  • the other end of the two ends of the heat exchanger is preferably linked to the removal point for the exhaust gas and/or the charge air.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas diverted at the removal point and/or the charge air can flow or do flow through the heat exchanger in opposite directions.
  • a heat exchanger of this type is also called a U-flow heat exchanger.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that the branch line is connected to one end of the heat exchanger, which is linked to the removal point for the exhaust gas and/or the charge air. It is achieved thereby that the exhaust gas, diverted at the removal point and not returned to the return point, flows through the heat exchanger multiple times. The heat recovery can be improved further thereby.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that a return line is connected to the other end of the two ends of the heat exchanger.
  • a filter can be arranged in the return line.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that a back pressure valve is connected downstream of the removal point.
  • the back pressure valve is used to build up back pressure at the removal point.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that an additional removal point, which can be connected via another exhaust gas recirculation valve to another return point, which is provided between the return point and the internal combustion engine, is provided between the internal combustion engine and the removal point.
  • An uncooled recirculation of the exhaust gas is made possible thereby in a simple manner.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that between the return point and the internal combustion engine a compressor for the exhaust gas and/or the charge air is provided, which is driven by a turbine, which is provided between the internal combustion engine and the removal point.
  • the additional removal point is preferably provided between the internal combustion engine and the turbine.
  • the additional return point is preferably provided between the compressor and the internal combustion engine.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that a charge air cooler is connected between the compressor and the internal combustion engine.
  • the additional return point is preferably provided between the charge air cooler and the internal combustion engine.
  • Another exemplary embodiment of the exhaust gas recirculation system is characterized in that a diesel particle filter is connected downstream of the turbine.
  • the diesel particle filter is preferably connected between the turbine and the removal point.
  • FIG. 1 shows a simplified illustration of an exhaust gas recirculation system of the invention with an internal combustion engine and a heat exchanger;
  • FIG. 2 shows the heat exchanger of FIG. 1 in an I-flow design in an exhaust gas recirculation mode
  • FIG. 3 shows the heat exchanger of FIG. 2 in a heat recovery mode
  • FIG. 4 shows the heat exchanger of FIG. 1 in a U-flow design in the heat recovery mode
  • FIG. 5 shows the heat exchanger of FIG. 4 in the exhaust gas recirculation mode.
  • FIG. 1 An exhaust gas recirculation system 1 in the form of a simplified fluid circuit diagram is shown in FIG. 1 .
  • a fluid particularly air or a fuel/air mixture, is supplied in exhaust gas recirculation system 1 in a known manner at a point 2 .
  • the fluid is preferably supplied via a compressor 4 and optionally a charge air cooler 5 to an internal combustion engine 6 , which is also called a combustion engine.
  • a turbine 7 which is used, as indicated by a dashed double arrow 8 , to drive compressor 4 , is connected downstream of internal combustion engine 6 .
  • a diesel particle filter 9 for example, is connected downstream of turbine 7 .
  • the performance of internal combustion engine 1 depends on the cubic capacity, rotational speed, and the average fluid pressure, particularly gas pressure.
  • the filling of the combustion chambers can be improved considerably by charging of the internal combustion engine 6 and the engine performance increased thereby.
  • the fluid or fuel/air mixture or the air is precompressed totally or partially outside the cylinder of the internal combustion engine.
  • the exhaust gases drive the turbine and the turbine drives the compressor.
  • the compressor takes over the intake and supplies the engine with a precompressed fresh gas charge.
  • Charge air cooler 5 in the charge line dissipates the compression heat into the ambient air. As a result, the cylinder filling is improved further.
  • the exhaust gas released by the internal combustion engine is diverted at a first removal point 11 and a second removal point 12 .
  • the exhaust gas diverted at the first removal point 11 can be returned cooled via a first return line 13 , in which a first exhaust gas recirculation valve 14 is arranged.
  • the exhaust gas diverted at the second removal point 12 can be returned uncooled via a second return line 16 , in which a second exhaust gas recirculation valve 17 is arranged.
  • a heat exchanger 18 is connected downstream of the first exhaust gas recirculation valve 14 .
  • the exhaust gas diverted at first removal point 11 and cooled in heat exchanger 18 can be supplied again to internal combustion engine 6 via a heat exchanger return line 20 and via a first return point 21 .
  • the exhaust gas diverted at second removal point 12 can be returned again uncooled to internal combustion engine 6 via the second exhaust gas recirculation valve 17 via a second return point 22 .
  • First removal point 11 is connected between diesel particle filter 9 and a back pressure valve 24 , which serves to build up back pressure when needed at first removal point 11 .
  • Second removal point 12 is arranged between internal combustion engine 6 and turbine 7 .
  • First return point 21 is arranged between point 2 and compressor 4 .
  • Second return point 22 is arranged between charge air cooler 5 and internal combustion engine 6 .
  • a third return point 23 is connected downstream of back pressure valve 24 .
  • An arrow 25 indicates that the exhaust gas of internal combustion engine 6 is supplied to a preferably sound-absorbing exhaust system, which can comprise a catalytic device.
  • the exhaust gas recirculation is used to cool the exhaust gas as much as possible.
  • the returned exhaust gas no longer participates in the combustion in the internal combustion engine but heats up. Overall, the temperature in the internal combustion engine or the engine is reduced by the returned exhaust gas.
  • the formation of nitrous oxides, which are highly dependent on the temperature in the engine, can be reduced by lower temperatures in the engine.
  • a filter 26 can be arranged in the heat exchanger return line 20 .
  • Heat exchanger 18 according to an essential aspect of the invention comprises a diverter valve 28 , which is connected downstream of the first exhaust gas recirculation valve 14 . Diverter valve 28 makes sure that both the exhaust gas diverted at first removal point 11 and returned via heat exchanger return line 20 and the exhaust gas diverted at first removal point 11 and diverted via a heat exchanger branch line 19 for the purpose of heat exchange first flows through a heat exchanger block 29 of heat exchanger 18 , as indicated by an arrow 30 .
  • Heat exchanger 18 can be operated in two different modes. In an exhaust gas recirculation cooling mode, heat exchanger 18 operates preferably as an I-flow heat exchanger, to lower the temperature of the gas flow of the returned exhaust gas. In a heat recovery mode, the gas flow diverted from the returned exhaust gas is used to heat the coolant passed through the heat exchanger, particularly in a warm-up phase of the internal combustion engine. Diverter valve 28 of the invention enables in a simple manner the illustration of the two modes with only one heat exchanger.
  • heat exchanger 18 of FIG. 1 can be made as a one-way flow-through heat exchanger 40 , which is also called an I-flow heat exchanger.
  • Heat exchanger 40 comprises a one-way flow-through heat exchanger block 42 with a header box 43 at one end. Header box 43 has an inlet connection 44 , through which, as indicated by an arrow 45 , exhaust gas diverted at removal point 11 enters header box 43 .
  • a header box 46 is provided into which a diverter valve 48 with a valve flap 49 is integrated. Header box 46 has two outlet connections 51 , 52 , through which the exhaust gas flow passed through heat exchanger block 42 emerges depending on the position of valve flap 49 of diverter valve 48 .
  • valve flap 49 of diverter valve 48 blocks outlet connection 52 , so that, as indicated by arrow 53 and 54 , the entire volume flow passed through heat exchanger block 42 emerges from outlet connection 51 , to which heat exchanger return line 20 is preferably connected.
  • no gas emerges from outlet connection 52 , as indicated by a dashed arrow 55 .
  • Heat exchanger branch line 19 is preferably connected to outlet connection 52 .
  • the first return line 13 is preferably connected to inlet connection 44 .
  • valve flap 49 of diverter valve 48 is in its second extreme position in which, as indicated by arrows 56 and 57 , all of the exhaust gas flow passed through heat exchanger block 42 emerges through outlet connection 52 .
  • a dashed arrow 58 indicates that in this position of valve flap 49 , no exhaust gas emerges from outlet connection 51 .
  • Heat exchanger 60 Shown in simplified form in FIGS. 4 and 5 is a heat exchanger 60 with at least one partition wall, which is indicated by a dashed line 61 and divides a heat exchanger block 62 so that it can be flown through in a U-shaped manner in opposite directions.
  • Heat exchanger 60 at one end of heat exchanger block 62 comprises a header box 63 with an inlet connection 64 and an outlet connection 65 , as indicated by arrows.
  • a header box 66 is provided, into which a diverter valve 68 with a valve flap 69 is integrated.
  • Header box 66 comprises another outlet connection 72 through which, depending on the position of valve flap 69 of diverter valve 68 , exhaust gas does or does not exit.
  • valve flap 69 of diverter valve 68 closes the additional outlet connection 72 , so that, as indicated by arrows 73 , 74 , and 75 , the flow passes through heat exchanger block 62 in a U-shaped manner. No exhaust gas exits through outlet connection 72 , as indicated by a dashed arrow 76 .
  • the first return line 13 is preferably connected to inlet connection 64 .
  • Heat exchanger branch line 19 is connected to outlet connection 65 .
  • Heat exchanger return line 20 is connected to the additional outlet connection 72 .
  • valve flap 69 of diverter valve 68 is in a middle position in which the U-shaped flow, indicated in FIG. 4 of heat exchanger block 62 , is interrupted.
  • Arrows 77 , 78 , 79 , and 80 in FIG. 5 indicate that the exhaust gas flow entering through inlet connection 64 flows one-way through heat exchanger block 62 in an I-shaped manner and again leaves completely through outlet connection 72 .
  • a dashed arrow 81 in FIG. 5 indicates that in this position of valve flap 69 of diverter valve 68 , no exhaust gas emerges from outlet connection 65 .
  • valve flap 49 ; 69 of diverter valve 48 ; 68 intermediate positions are possible in which in each case only a fraction of the exhaust gas flow supplied through the first return line 13 reaches the heat exchanger return line 20 or heat exchanger branch line 19 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
US12/891,396 2009-09-25 2010-09-27 Exhaust gas recirculation system Expired - Fee Related US8572962B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EPEP09290726.0 2009-09-25
EP09290726.0A EP2302190B1 (fr) 2009-09-25 2009-09-25 Système de refoulement des gaz d'échappement
EP09290726 2009-09-25

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US8572962B2 true US8572962B2 (en) 2013-11-05

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8839518B1 (en) * 2010-12-16 2014-09-23 Kennieth Neal EGR cooler and method of rebuilding existing cooler
US20150135690A1 (en) * 2012-05-09 2015-05-21 Valeo Systemes De Controle Moteur System for recovering energy in an exhaust gas circuit
US20180156142A1 (en) * 2016-12-01 2018-06-07 Ford Global Technologies, Llc Method and system for exhaust gas recirculation and heat recovery
WO2021170250A1 (fr) * 2020-02-28 2021-09-02 Pierburg Gmbh Système de recirculation des gaz d'échappement pour moteur à combustion interne et procédé de commande d'un tel système de recirculation des gaz d'échappement

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8661799B2 (en) * 2010-10-13 2014-03-04 Ford Global Technologies, Llc Exhaust system for an internal combustion engine
US20140109884A1 (en) * 2012-10-23 2014-04-24 Daniel E Hornback Automotive engine coolant and heating system
US9631540B2 (en) * 2014-10-22 2017-04-25 Ford Global Technologies, Llc Exhaust system and methods for efficient exhaust heat recovery
DE102014223815A1 (de) * 2014-11-21 2016-05-25 Maha-Aip Gmbh & Co. Kg Abgasmessanlage zur Messung von Verbrennungsabgasen
US10184407B2 (en) * 2016-09-12 2019-01-22 Ford Global Technologies, Llc Method and system for emissions reduction
DE102016218990A1 (de) * 2016-09-30 2018-04-05 Ford Global Technologies, Llc Aufgeladene Brennkraftmaschine mit gekühlter Abgasrückführung
CN106499550A (zh) * 2016-11-28 2017-03-15 哈尔滨工程大学 一种船舶低速柴油机egr冷却器s‑co2循环余热利用系统
DE102017111101B4 (de) * 2017-05-22 2020-06-25 Pierburg Gmbh Abgasrückführvorrichtung für eine Verbrennungskraftmaschine mit Wärmetauscher zur Energierückgewinnung

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US5927075A (en) * 1997-06-06 1999-07-27 Turbodyne Systems, Inc. Method and apparatus for exhaust gas recirculation control and power augmentation in an internal combustion engine
US6155042A (en) 1997-10-31 2000-12-05 Valeo Thermique Moteur Exhaust gas recirculation line for an automobile engine
DE10259702A1 (de) 2001-12-27 2003-07-17 Denso Corp Abgassystem für einen Wärmemotor
EP1405995A1 (fr) 2002-10-02 2004-04-07 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Moteur suralimenté par un turbocompresseur à recirculation de gaz d'échappement ainsi que le procédé de fonctionnement de celui-ci
DE10392766T5 (de) 2002-06-04 2005-06-16 Valeo Thermique Moteur Abgasleitung für einen Brennkraftmotor mit einer thermischen Regelung der Abgase
US7043914B2 (en) * 2002-11-15 2006-05-16 Isuzu Motors Limited EGR system for internal combustion engine provided with a turbo-charger
FR2892770B1 (fr) 2005-10-28 2008-01-18 Renault Sas Dispositif de recirculation controlee des gaz brules d'un circuit egr a haute pression
EP2025912A1 (fr) 2007-07-30 2009-02-18 Peugeot Citroen Automobiles SA Circuit des gaz d'échappement d'un moteur
US8297049B2 (en) * 2006-03-16 2012-10-30 Toyota Jidosha Kabushiki Kaisha Exhaust gas heat recovery device

Patent Citations (11)

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Publication number Priority date Publication date Assignee Title
US5927075A (en) * 1997-06-06 1999-07-27 Turbodyne Systems, Inc. Method and apparatus for exhaust gas recirculation control and power augmentation in an internal combustion engine
US6155042A (en) 1997-10-31 2000-12-05 Valeo Thermique Moteur Exhaust gas recirculation line for an automobile engine
EP0913561B1 (fr) 1997-10-31 2003-08-20 Valeo Thermique Moteur S.A. Ligne d'échappement et de recirculation des gaz pour moteur de véhicule automobile
DE69817294T2 (de) 1997-10-31 2004-06-09 Valeo Thermique Moteur S.A. Auspuff- und Abgasrückführungsleitung einer Brennkraftmaschine
DE10259702A1 (de) 2001-12-27 2003-07-17 Denso Corp Abgassystem für einen Wärmemotor
DE10392766T5 (de) 2002-06-04 2005-06-16 Valeo Thermique Moteur Abgasleitung für einen Brennkraftmotor mit einer thermischen Regelung der Abgase
EP1405995A1 (fr) 2002-10-02 2004-04-07 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Moteur suralimenté par un turbocompresseur à recirculation de gaz d'échappement ainsi que le procédé de fonctionnement de celui-ci
US7043914B2 (en) * 2002-11-15 2006-05-16 Isuzu Motors Limited EGR system for internal combustion engine provided with a turbo-charger
FR2892770B1 (fr) 2005-10-28 2008-01-18 Renault Sas Dispositif de recirculation controlee des gaz brules d'un circuit egr a haute pression
US8297049B2 (en) * 2006-03-16 2012-10-30 Toyota Jidosha Kabushiki Kaisha Exhaust gas heat recovery device
EP2025912A1 (fr) 2007-07-30 2009-02-18 Peugeot Citroen Automobiles SA Circuit des gaz d'échappement d'un moteur

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8839518B1 (en) * 2010-12-16 2014-09-23 Kennieth Neal EGR cooler and method of rebuilding existing cooler
US20150135690A1 (en) * 2012-05-09 2015-05-21 Valeo Systemes De Controle Moteur System for recovering energy in an exhaust gas circuit
US20180156142A1 (en) * 2016-12-01 2018-06-07 Ford Global Technologies, Llc Method and system for exhaust gas recirculation and heat recovery
US10107213B2 (en) * 2016-12-01 2018-10-23 Ford Global Technologies, Llc Method and system for exhaust gas recirculation and heat recovery
US10578036B2 (en) 2016-12-01 2020-03-03 Ford Global Technologies, Llc Method and system for exhaust gas recirculation and heat recovery
WO2021170250A1 (fr) * 2020-02-28 2021-09-02 Pierburg Gmbh Système de recirculation des gaz d'échappement pour moteur à combustion interne et procédé de commande d'un tel système de recirculation des gaz d'échappement

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CN102032073A (zh) 2011-04-27
EP2302190B1 (fr) 2013-12-25
US20110072808A1 (en) 2011-03-31
EP2302190A1 (fr) 2011-03-30

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